Change-speed gear



Nov. 114, 1939.

W. MELLER CHANGE-SPEED GEAR Filed March 5, 1955 4 Sheets-Sheet 1 W. MELLER Nov. 14, 1939.

CHANGE-SPEED GEAR Filed March 5, 1935 4 Sheets-Sheet 2 14-, $939. w, MELLER ,179.827

CHANGE-SPEED GEAR Filed March 5, 1935' 4 Sheets-Sheet 3 Fig, '9

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M/VENTOR BY 0861/ 624 A TTOR NE YS 0v, M, 1939. w. MELLER 2'1791827 CHANGE-SPEED GEAR Filed March 5, 1955 4 Sheets-Sheet 4 Patented Nov. 14, 1939 STATES PATENT OFFICE Application March 5, 1935, Serial No. 9,370- In Germany January 12, 1934 3 Claims. (01. 74-111) This inventioncrelates to a change-speed gear, in which an eccentric or similar driving member, acts upon the driven shaft through one or more swing members or link motions, which are rotatably supported in a stationary position, and of which their oscillating rotary movement, is transmitted to the driven shaft or shafts by means of toothed wheels and ratchet and pawl or similar mechanisms. Y

The main object of this invention is to provide a change-speed gear which is simple and efficient and has the advantage of being free of vibrations and noises. An essential advantage obtained by my invention is the fact, that any kind of output speed characteristic of the driving engine can be transformed into any other kind of torque-speed characteristic of the driven machine. Furthermore, the invention renders possible a change from forward to backward running, a free running and braking in both directions, a deviation of the centre lines of the driving and driven shafts; the greatest equalizations of irregularities in the drive; the raising or reducing of the speed ratio at will; and finally a construction which economises space and constituents, more particularly owing to the fact that the amplitude of the oscillations is made usable in both directions.

The invention is illustrated by way of example in the accompanying drawings, in which- Figure 1 shows one example of the invention in longitudinal section, partly on the line A-0 and partly on the line 3-0 in Figure 2;

Figures 2 and 3 are cross sections on the lines C-D, E--F respectively in Figure 1;

Figure 4 is a diagrammatic view of the centrifugal governor and driver;

Figure 5 shows an alternative regulating means as a modification of a detail in the iongitudinal' section of Figure 1;

Figures 6, 6a and 6?) illustrates three diflerent positions of a clutch control mechanism;

Figure '7 shows a perspective and enlarged view of the centrifugal governor and driving member;

I Figure 8 shows a centrifugal rock member;

Figure 9 is a sectional sideview of a modified speed gear provided with four driven shafts and drawn on line ii9, Figure 10; and

Figure 10 is a sectional plan view of same on line lit-til, Figure 9.

Referring to the drawings- The driving shaft I and the driven shaft 2 are so supported in a casing t that an angular deviation between the two is possible. Bearing brasses, sets of balls, lubrication, m sitioning rings and so forth are for the most part omitted in the drawings for the sake of clearness.

. With' shaft l rotates a centrifugal governor comprising, a centrifugal weight-concentric 4 provided with a rectangular slot i I, Fig. 9, which is connected with a counterpoise 5 by a rod mechanism which is in the nature of a double scissors joint. Said rod mechanism consists of two rings 60, which are loosely arranged in a sleeve keyed on the driving shaft I and are provided with lugs 6|, 6! (Fig. '7) connected with each other by links 6. The bolts 62 (Fig. 1) connecting the links 6 with each other e inserted through openings in the weight 4 an the counterpdise 5 respectively and hold the parts of the governor together, which is slidably arranged on the square portion I ID of the shaft I by means of the rectangular slot 4 l I. The centrifugal force of both members 4 and 5 is opposed by springs I one end of which being secured to the members 4 and 5 respectively, the other end being attached to bell crank levers 8, which are pivpendulum ball bearing, rotatably held in square block H, which in its turn moves within a swing member in form of a prismaticguidebar it, fast to a shaft it.

vDuring the operation of the centrifugal oscillating mechanism, the weight-eccentric 4, en-

gaging the, square of main shaft II, is constantly kept in rotation. It will be inefiective if its centre line falls together with the centre of the main shaft. If however the speed of this shaft is increased above a maximum, the centrifugal force of the weight-eccentric will overcome that of springs '71. The weight-eccentric is displaced from its central position and a consequent eccentric action on the rock member or frame it, will os cillate the latter. I

To counteract the unbalanced effect on the main shaft, the counter weight 5, interconnected with weight t, by means of link mechanism b, will automatically respond and equalize the forces. a

To pivot it at the centre of oscillation are keyed the ratchet hubs iii, opposed to one another like mirror images, in such a way that they drive toothed wheels i5 and it by means of the rollers in one' direction of rotation, and drive toothed wheels is and i"! in the other direction. The toothed wheels it and it mesh directly with I8, through the medium of idle reversing wheels 2|, act upon rings of teeth 2|, which are firmly screwedto clutch members 22 and to the toothed wheels l9. These two methods of transmitting rotation from the oscillating central pivots l3 to the driven shaft 2, which have here been described collectively, are in part superfluous, and,

although they are also to be employed in certain cases in the assembly set forth, according to the purpose for which they are to be used, either the toothed wheels I6 and It or the toothed wheels I! and I8, together with the toothed wheels I! or 20 and, 2| meshing therewith at times, and

also the clutch member 22, may be omitted for the purpose of saving expense.

The clutch members 23, keyed on to-the driven shaft'in a longitudinally movable manner, are actuated by switch lever arms '24 and a double cam disc 25, in such a way that upon one or other of them being engaged, Fig. 6, one direction of rotation is attained in each case, while byputting in both a braking action is attained, and

by disconnecting both a free running of the driven shaft occurs. This shifting may be controlled by the pivot 260i the cam disc 25, and by chain wheels 21 and a chain 28 connected to a control shaft 2'", from any convenient place outside the coupling. Control shaft 2'", or the cam shaft 26, are capable of actuating other members, as for instance independent brakes, regulating members of the driving engine and so forth, as well as the adjusting lever Ill. The number of oscillating members, which may be freely selected, and the angle of the mid positions A-O and B of the oscillating members in relation to the main axes, that is to say, asymmetrical arrangement of the swinging members or the central pivots thereof, in relation to one another and in relation to the main axes of the primary and secondary shafts, as well'as the distances A-O and B0 and the transmission ratios (numbers of teeth) of the toothed wheels, admit of being advantageously determined on account of the drive being non-uniform", by analyzing the same into components on the mathematical principle of Fourier.

In the case illustrated in Figs. 1 to 4 and 7 to 10, the transmission is regulated by the changes in speed of revolution of the driving shaft. If. however, the regulating is to be effected in dependence upon the speed of revolution 01' the driven shaft,'the centrifugal governor 4 to 8 is arranged (Fig. on this shaft, whereas the eccentric, which formerly consisted of one piece, with the governor weight, in this case remains an independent part {a 'upon the driving shaft. The

deflection of the weight I displaces, by means of a lever 3|, a'disc 29 slidably arranged upon the driven shaft, whereby the bell-crank lever 3|, which is rotatably mounted upon the hub 32 keyed to the driving shaft 1, increases or diminishes the eccentricity of the eccentric In. according to the purpose for which it is to be employed. A spring 13, one end of which being connected with the bell-crank lever 3|, the other end of which being attached to the hub 32, urges the lever 3i positively against said disc 29. The other parts of the device are the same as those shown in Figs. 1 to 4.

- If a plurality of shafts are to be driven at the same time, Figs. 9 and '10 the hubs l4 upon every other central oscillation pivot 13, which here can only be employed in an even number; .are oppositely keyed on, and all the toothed wheels ii are so arranged as to mesh with one another in succession. The toothed wheels I6 are arranged in the same way but rotate in the opposite direction. The toothed wheels l9 maynow mesh in pairs, to any desired number, only limited by the space available, with eachof the pairs of toothed wheels l5 and I 6, the control members admitting of being employed either in-' dividually for each shaft 2 or else coupled together, and being mounted on every other central swing pivot, to correspond to cam discs 25 reversed like mirror images. The employment of differently designed elements,'such for example as toothed wheels with inclined or arrow-shaped teeth, centrifugalregulators of other types, and

so forth, does not in any way affect the princiwheels, one of these ratchet mechanisms rotating one of the said wheels when the shaft is oscillating in one direction and the other ratchet mechanism rotating the other wheel when the rock shaft is oscillating in the other direction, and engageable and disengageablecoupling means for communicating rotary motion from the said wheels to the driven shaft.

2. A change-speed gear as claimed in claim 1, further comprising a single manipulating organ, such as a gear lever, for engaging and disengaging the said coupling means.

3. A change-speed gear as claimed in claim 1, the coupling means being adapted to produce a braking action by coupling the driven shaft to both the transmission wheels at the same time. WILLIAM MELLER; 

